Electromagnetic brake wtih rotational structure for wear adjustment

ABSTRACT

An electromagnetic brake is disclosed comprising a brake wheel, at least one friction surface attached to a respective friction plate and urged into frictional engagement with the brake wheel during braking. An electromagnet and an anchor serve to disengage the friction surface from the brake wheel when a current is supplied to the electromagnet. To compensate for the wear of the friction surface, the anchor is adapted to rotate in adjustment threads and thereby advance towards the magnet. Rotation of the anchor is caused by a coil spring. To maintain an essentially constant clearance between the electromagnet and the anchor when the brake is in the close state, the brake is provided with spring-loaded lugs mounted on a face of the anchor and protruding a predetermined distance towards the electromagnet. The spring-loaded lugs are adapted to limit the movement of the anchor towards the electromagnet when the brake is closed, and is compressed to allow the brake to be disengaged when power are supplied to the electromagnet.

This is a divisional of application Ser. No. 07/976,007, filed Nov. 3,1992, now U.S. Pat. No. 5,368,738, which in turn is a continuation ofprior application Ser. No. 07/668,564, filed Mar. 13, 1991, abandoned.

The present invention relates to an electromagnetic brake which isreleased by the action of the electromagnet when power is supplied tothe electromagnet, and engaged when power supply to the electromagnet iscut off.

In electro magnetic disc or drum brakes, the working clearance betweenthe electromagnet and the anchor plate (when the brake is in the closedposition) tends to increase, due to the wear of the friction surfacesand the brake wheel. An increase in this working clearance leads to adecreased force of attraction between the electromagnet and the anchorplate, and consequent difficulties in releasing the brake. Anotherconsequence of this increased working clearance is a decreased brakespring force, which results in a reduced brake torque. In addition, alarge working clearance increases the speed of the anchor plate movement(thus increasing the impact force applied to the friction surfaces) whenthe brake is being engaged. The result of this is a high initial peak inbraking torque which imposes a high stress on the brake and otherstructures and deteriorates the operating characteristics of the brake.Moreover, the reliability of the brake suffers due to the higher stresslevel, and the stresses may become uncontrollable due to insufficientservicing.

FI publication 75653 proposes an electromagnetic disc brake in which,when the brake is closed, a constant gap between the electromagnet coiland the anchor plate is maintained by means of a stepless adjustingdevice. This adjusting device is provided with balls running in groovetracks at that end where the electromagnet frame is located. Analternative adjusting device employs a wedge placed between the frameand the electromagnet coil. The wedge moves down-wards due to its ownweight, thereby adjusting the size of the gap.

An object of the present invention is to provide an electromagneticbrake in which means is provided for improved adjustment of the workingclearance.

According to the present invention, an electromagnetic brake has a brakewheel supported on a shaft, and friction surfaces fixedly secured onrespective friction plates. The friction plates are forced, by urgingmeans, into frictional engagement with the brake wheel when theelectromagnetic brake is closed. The electromagnetic brake also includesanchor means rotatably mounted in a frame. Electromagnet means arefixedly secured to at least one of the friction plates, theelectromagnet means being arranged in cooperative, spaced relation tothe anchor means. When current is supplied to the electromagnet means,the electromagnet means moves toward the anchor means so as to releasethe friction surfaces from the brake wheel. The electromagnet brake alsoincludes means for compensating for any attendant wear of the frictionsurfaces, thereby maintaining a substantially constant, predeterminedclearance between the electromagnet means and the anchor means when theelectromagnetic brake is closed. Furthermore, the compensating meansincludes thread means for allowing the anchor means to advance towardthe electromagnet means when the anchor means is rotated in apredetermined direction. Rotating means are provided for effecting theabove described rotation. Stopping means are also provided for stoppingthe advance of the anchor means when the distance between theelectromagnet means and the anchor means is substantially equal to theabove mentioned, predetermined clearance.

The invention achieves a brake with a substantially constant air gap,which means that a smaller brake electromagnet can be used. Moreover,the brake permits the presence of a large number of tolerances, and theworking clearance can be adjusted by the stopping means, for example,spring loaded pins. The adjustment is even and simple, and remainsfunctional through at least the range of motion required to accommodatewear of the friction surfaces.

BRIEF DESCRIPTION OF THE DRAWINGS

In the following, the invention is described in detail by the aid ofexamples referring to the attached drawings, in which:

FIG. 1 illustrates in cross-section a disc brake according to a firstembodiment of the invention;

FIGS. 2a and 2b respectively show face and side views of the anchorplate of a disc brake according to the invention;

FIG. 3 shows a side view of an adjusting plate of the disc brakeaccording to the invention;

FIGS. 4a through 4d illustrate, respective cross sectional views of adisc brake;

FIG. 5 illustrates a portion of a drum brake according to a thirdembodiment of the invention;

FIG. 6 illustrates a cross-section of a disc brake according to a fourthembodiment of the invention;

FIGS. 7a and 7b respectively show face and cross-sectional views of theadjusting lugs on the friction plates of the embodiment illustrated inFIG. 6;

FIGS. 8a-8c illustrate in cross-section, adjustment of the alignment ofthe friction plate in the brake according to the embodiment illustratedin FIG. 6;

FIGS. 9a and 9b respectively illustrate face and cross-sectional viewsof the adjustment ring in the brake according to the embodimentillustrated in FIG. 6.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

FIG. 1 illustrates in cross-section an electromagnetic brake in whichthe working clearance between the brake and the electromagnet isself-adjusting. This type of brake is typically employed with anelectric motor which may be used, for example, as a hoisting motor in acrane. The brake comprises an end shield 1, on which is disposed a firstset of friction plates 2. A second set of friction plates 3 is coupledto an electromagnet, which is formed as a substantially U-shaped annularelectromagnet housing 7, and a electromagnet winding 8 disposed insidethe groove of the housing 7. The electromagnet housing 7 is adapted tothe brake housing 19 such that it can move in the axial direction, butis prevented from rotation. The groove of the electromagnet housing 7 issubstantially covered by an anchor plate 9, which is rotatably adaptedto the brake housing 19. The electromagnet housing 7 and the anchorplate 9 remain separated in the axial direction by a small distance. Thefriction plates 2 and 3, are provided with respective friction surfaces4 and 5. Interposed between the friction plates 2 and 3, is a brokenwheel 6.

When the electromagnet receives current through the conductor 10, themagnetic force acting between the electromagnet and the anchor plateforces the electromagnet housing 7 and the anchor plate 9 together. Theanchor plate is provided with three pitched vanes 11a-11c, asillustrated in FIGS. 2a and 2b, which are rotatably engaged in a flatthread composed of three pitched tracks formed by two identical matingadjustment rings 12a and 12b. The adjustment rings 12a and 12b arefixedly adapted to the brake housing 19, and are each provided withthree flat-thread track surfaces 13 as illustrated in FIG. 3.

The anchor plate 9 may be rotated by means of a coiled spring 14 woundabout a spring box 15 disposed on, and co-axially to, the anchor plate9. The anchor plate 9 is provided with holes 16a-16c, as illustrated inFIG. 2a, which accommodate pins 17 loaded by a pre-tensioned spring (notshown), for example a cup spring. The pins 17 pass through the anchorplate 9, and extend towards the electromagnet housing 7 a distanceequalling the working clearance e.

When no current is flowing in the brake electromagnet winding 8, themagnet-friction plate assembly is urged into frictional engagement withthe brake wheel 6 by the brake springs 18, which bear against the brakehousing 19, and braking action is started. At this instant, there is acertain working clearance between the electromagnet housing 7 and theanchor plate 9. This clearance nominally equals the length of theprotruding parts of the pins 17 minus the anchor plate tolerance. As thebraking surfaces get thinner due to wear, however, the clearance betweenthe electromagnet housing 7 and anchor plate 9 increases. In response,the coiled spring 14 causes the anchor plate 9 to rotate in its threadtracks, and thereby advance toward the electromagnet housing 7, untilthe pin ends meet the electromagnet housing 7. Because the force of thecoiled spring 14 does not exceed the force of the cup spring pressingthe pins out through the anchor plate 9, the adjusting motion of theanchor plate 9 is stopped when the pin ends meet the electromagnethousing 7. Thus the wear of the brake surfaces has been compensated.Note that because the anchor plate advances smoothly as it rotates, thecompensation is stepless.

The next time the power to the electromagnet is switched on, anattractive force is generated between the electromagnet and the anchor.Because the anchor plate 9 is in a self-retaining thread, the anchorplate 9 cannot move parallel to the axle 20. The electromagnet housing 7is moment-locked, and thus cannot rotate, but is adapted to slidecoaxially to the axle 20. The force of attraction between theelectromagnet housing 7 and the anchor plate 9 exceeds the sum of theforce of the brake springs 18 and the pressure of the pins 17, and thusstarts moving the electromagnet housing 7 towards the anchor plate 9,pressing in the pins 17 against the force of the cup spring. Theclearance between the electromagnet housing 7 and the anchor plate 9 isthereby reduced to nil. The backward movement of the electromagnethousing 7 produces a working gap between the friction plates 2 and 3 andthe brake wheel 6, thereby releasing the brake. An auxiliary spring 21distributes the working gap evenly on either side of the brake wheel.

When the current to the electromagnet winding 8 is cut off, the force ofattraction between the electromagnet housing 7 and the anchor platecollapses, and the force of the brake springs 18 suddenly drives thefriction plates 2 and 3 into engagement with the brake wheel.

To damp the effects of impacts between the anchor 9 and theelectromagnet housing 8, the brake may be provided with a circularspring 22 placed in front of the foremost adjustment ring 12a.

In an alternative arrangement, instead of placing the pins 17 in theanchor plate 9, the pins can be placed in the electromagnet housing 7and adapted to bear against the anchor plate 9.

In a further alternative, the anchor plate 9 may be provided with anexternal thread instead of the pitched vanes 11a-11b, and placed insidean internally threaded adjustment ring instead of the mating adjustmentrings 12a and 12b, so that the anchor plate 9 may turn inside theadjustment ring according to the degree of wear of the friction plates 2and 3 in a manner similar to that described above.

In the embodiment illustrated in FIG. 4a, one of the friction plates 23also serves as an anchor plate, with spring elements 24 pressing thepins 17 against the electromagnet housing 25. In this case, the grooveof the electromagnet housing 25 points towards the motor. Theelectromagnet housing 25 is provided with an external thread 26, whichengages with the internal thread 28 of an adjustment ring 27 adapted tothe brake housing 19. The conductor 29 passes round the axle 20 inside aprotective shield 30.

In this embodiment, the friction plate 23 is adapted to slide co-axiallywith the shaft 20, but is prevented from rotation. The electromagnethousing 25 may be urged to rotate by the spring 14 and thereby advancethe electromagnet housing 25 toward the friction plate 23 until the pins17 meet the electromagnet housing 25. When power is supplied to theelectromagnet winding 8, the friction plate 23 is urged backwards,depressing the pins 17, opening a gap between the friction plates 2 and23 and the brake wheel 6, and thereby releasing the brake. When thepower supply to the electromagnet winding 8 is cut off, the brakesprings 18 urge the friction plates 2 and 23 into frictional engagementwith the brake wheel 6, and braking action begins.

FIGS. 4b-4d illustrate respective variations of the embodiment of FIG.4a. In FIG. 4b, the spring-loaded pins 17 of FIG. 4a are replaced byspring-loaded pins mounted in the electromagnet housing 25 andprojecting toward the friction plate 23. This variation will, of course,function in a manner which is essentially identical to that of theembodiment of FIG. 4a.

In FIG. 4c, the spring loaded pins 17 are replaced by a resilient O-ringmounted in a groove disposed on the face of the electromagnet housing 25and projecting towards the friction plate 23. In FIG. 4d, the springloaded pins 17 are replaced by a resilient O-ring mounted in a groovedisposed on the face of the friction plate 23 and projecting towards theelectromagnet housing 25. In both of the variations illustrated in FIGS.4c and 4d, the O-ring provides an additional damping function, which isdiscussed in greater detail below in connection with FIGS. 6-8.

FIG. 5 illustrates an automatically adjusted drum brake according to athird embodiment of the invention. The brake is provided with brake arms32 actuated by push/pull rods 31. The ends of the brake arms areprovided with brake linings 33 which engage the brake drum 34 duringbraking. Brake springs 35 disposed between the frame 36 and stoppers 37apply a tensile force to the push/pull rods 31, and thereby urge thebrake linings 33 into frictional engagement with the brake drum 34. Asthe brake linings 33 wear, the width of the air gap between the anchor38 and the electromagnet housing 40 tends to increase due to thereduction of the thickness of the brake linings 33. The anchor 38 isrotatably connected to the ends of the push/pull rods 31 by threads 41and 42, and urged to rotate with respect to the push/pull rods 31 byrespective coiled springs 43. The anchor plates 38 are fitted with holesthrough which are movably disposed pins 45 which are urged through theanchor plates 38 towards the electromagnet housings 40 by cup springs44. When the power to the electromagnet windings 39 is disconnected, thecoiled springs 43 cause the anchors 38 to rotate on the threads 42 ofthe push/pull rods until the spring-loaded (cup springs 44) pins 45 meetthe electromagnet surface.

Guide bushings 46 ensure that the anchor faces are always aligned in adirection sufficiently close to parallel with the correspondingelectromagnet surfaces. The adjusting threads 41, 42 must beself-retaining. Note that, as can be seen in FIG. 5, the two halves ofthe drum brake are symmetrical.

FIG. 6 illustrates in cross-section a disc brake according to a fourthembodiment of the invention. When power to the electromagnet winding 8is cut off, the brake springs 18 press the friction plate54/electromagnet assembly against the brake wheel 6. The brake wheel 6is supported on the shaft 20 by splines 47 which enable the brake wheel6 to move axially, thus allowing the brake wheel 6 to be pressed againstboth friction plates 2 and 54 evenly during braking.

As a result of wear during braking, the friction surfaces 4 and 5 areworn down, and consequently the clearance between the electromagnethousing 8 and the anchor 54 increases. If no compensation for the wearis provided, the clearance will eventually become too large for themagnetic attraction to release the brake.

In this embodiment, the outer surface of the anchor 48 is provided witha thread which engages a corresponding thread provided in the brakehousing 49. Therefore, the anchor 48 is able to rotate, and thereforeadvance, in the thread of the brake housing 49. To rotate the anchor 48,the brake is provided with a coiled spring 50 accommodated in a separatespring box 51 provided on the end face of the anchor 48. The spring box51 protects the spring against entanglement and accidental unwinding aswell as against hitting other parts of the brake. The outer end of thecoiled spring 50 can be fastened with a screw 52, at a selectablelocation, to the brake housing 49. For this purpose, the brake housing49 is provided with holes or cut-outs disposed at a constant radius fromthe axis of the motor axle, and angularly separated by 15°.

As the clearance between the electromagnet housing 7 and the anchor 48gradually increases due to wear, the coiled spring 50 rotates the anchor48 until the latter touches an elastic O-ring 53 accommodated in agroove disposed in the face of the electromagnet housing 7.

The O-ring 53 is mounted so that it protrudes beyond the surface of theelectromagnet housing 7 by a predetermined distance. When the anchor 48touches the O-ring 53, the high frictional force generated between therubber O-ring 53 and the steel anchor 48 prevents further rotation (andtherefore advancement) of the anchor 48.

Due to the resiliency and high frictional co-efficient of the O-ring 53,the problem of over-compensation is reduced. Over-compensation resultswhen repeated impacts between the adjusting threads on the anchor 48 (orthe electromagnet housing 7) and the brake housing 49 (or the adjustmentring 12a-12b) causes undesired rotation (and therefore advance) in theadjustment threads. This impact-induced advancement has the effect ofover-compensating for the wear of the friction surfaces 4 and 5. In theextreme, this over-compensation may reduce the working clearance to nil,thereby rendering the brake inoperative by preventing the electromagnet7 and 8 from releasing the brake.

When an electric current is supplied to the electromagnet winding 8, amagnetic attraction is set up between the electromagnet and the anchor48. The attraction first eliminates the axial clearance between thethreads on the anchor 48 and brake housing 49. Then the electromagnethousing 7/friction plate 54 assembly is pulled back towards the anchor48 as the O-ring 53 is compressed. Thus, the width of the clearance inwhich the brake wheel 6 rotates equals the O-ring 53 protrusion minusthe axial clearance between the threads.

Since the attractive force of the brake electromagnet increases as theworking clearance is reduced, it is advantageous to make the workingclearance as narrow as possible. This allows minimization of theelectromagnet size and the associated costs. However, the use of aminimal working clearance requires a high degree of control over theworking clearance of the brake wheel 6 to ensure that the workingclearance will not become too narrow. This high degree of controlrequires that the working clearance should not be greatly reduced due toclearances and manufacturing tolerances in other components of thebrake.

In this embodiment, the joint between the electromagnet housing 7 andone of the friction plates 54 has no play. This is achieved by"calibrating" the thickness of the friction plate 54. The calibration isimplemented by bending small collets 55 (FIGS. 7a-b and 8a-c) outwardsfrom the plane of the plate. Calibration is necessary because thethickness of standard steel plate varies too much to permit adequatecontrol over the width of working clearance, and proper alignment of thefriction plate with the brake wheel. For example, in the case of 4 mmhot rolled steel plate, the allowed thickness variation is +0.6 mm and-0.4 mm (DIN 1543).

Without calibration of plate thickness, the axial space for the frictionplate 54 on the outer surface of the electromagnet housing 7 should bedetermined according to the largest permitted plate thickness. In theworst case, this would lead to an additional axial clearance as large as1 mm (in the case of minimum allowed plate thickness).

Referring to FIGS. 9a and 9b, the brake housing adjusting thread whichengages the anchor adjusting thread is not continuous but is dividedinto four sections 56a-56d. Regardless of the motor position, themidpoints of these sections are always at an angle of 45° relative tothe horizontal and vertical axes. This arrangement allows the dust anddirt accumulated in the threads to fall down from the thread. Thus thethreads in the brake housing 49 are self-cleaning. The self-cleaningeffect is promoted by the axial anchor motion which occurs each timepower to the electromagnet is switched on or off.

The brake housing 49 is also provided with a cut-out for the brakeelectromagnet supply cable. This cut-out accommodates a cable sealwhich, besides sealing the cable, also prevents the electromagnetwinding 8 from rotating. Prevention of rotation of the electromagnetwinding 8 is necessary to ensure correct operation of the adjustmentmechanism and to protect the cable against damage by attrition. Thesevarious holes and cut-outs in the electromagnet housing 7 describedabove also allow auxiliary equipment and attachments to be fastenedthereto without extra machining.

The brake housing 49 is also provided with lugs (not illustrated) which:

position the brake housing 49 in the axial direction;

permit moment-locking of the brake parts by means of screws; and

protect the friction plate lugs against impacts.

Furthermore, as shown in FIG. 9b, the brake housing 49 comprises sleeves57 placed inside the brake springs 18 and provided with an internalthread. By inserting threaded bolts 58 through corresponding holes inthe brake housing and screwing them into the sleeves 57, the brakesprings 18 can be prevented from being released when the brake isdismantled, for example in connection with maintenance operations.

Instead of using an O-ring 53, a variety of other shapes may beemployed. For example, the O-ring may be replaced by a plurality ofbands composed of a material with elastic properties similar to that ofthe O-rings. Similarly, short bars, pins, or balls accommodated inappropriately shaped cut-outs disposed on the face of the electromagnethousing 7 may also be used without adversely affecting the operation ofthe brake or adjustment system.

In addition, in the above description, the O-ring 53 (or other elasticmembers as described above) has been described as being accommodated onthe face of the electromagnet housing 7. However, it may also beoperatively accommodated on the face of the anchor 48.

Thus it will be apparent to a person skilled in the art that differentembodiments of the invention are not restricted to the examplesdescribed above, but that they may instead be varied within the scope ofthe following claims.

I claim:
 1. An electromagnetic brake having a brake wheel disposed on ashaft, and friction surfaces fixedly disposed on respective frictionplates, said friction plates being forced by urging means intofrictional engagement with said brake wheel when said electromagneticbrake is in an engaged condition, said electromagnetic brakecomprising:electromagnet means rotatably mounted in a substantiallyfixed frame of said electromagnetic brake; anchor means comprising oneof said friction plates, said anchor means being disposed in cooperativespaced relation to said electromagnet means whereby said anchor meansmoves toward said electromagnet means so as to disengage said frictionsurfaces from the brake wheel when a current is supplied to saidelectromagnet means; and compensating means for compensating for thewear of said friction surfaces and thereby maintaining a substantiallyconstant predetermined clearance between said electromagnet means andsaid anchor means when the electromagnetic brake is in the engagedcondition, said compensating means comprising thread means substantiallyfixedly disposed on said brake frame and adapted to permit saidelectromagnet means to advance toward said anchor means when saidelectromagnet means is rotated in a predetermined direction in saidthread means, rotating means for urging rotation of said electromagnetmeans in said predetermined direction, and stopping means for stoppingthe rotation of said electromagnet means in said thread means when thedistance between said electromagnet means and said anchor means issubstantially equal to said predetermined clearance.
 2. A brake asclaimed in claim 1, wherein said thread means comprises an adjustmentring substantially fixedly attached to the brake frame, an inner surfaceof said ring being provided with a thread operatively engagable with amatching thread disposed on a peripheral surface of said electromagnetmeans.
 3. A brake as claimed in claim 1, further comprising dampingmeans disposed between said electromagnet means and said anchor means,said damping means serving to damp impact between said electromagnetmeans and said anchor means when said stopping means stops the rotationof said electromagnet means in said thread means when the distancebetween said electromagnet means and said anchor means is substantiallyequal to said predetermined clearance.
 4. A brake as claimed in claim 3,wherein said damping means comprises a resilient O-ring disposed on asurface of said anchor means and projecting towards said electromagnetmeans.
 5. A brake as claimed in claim 3, wherein said damping meanscomprises a resilient O-ring disposed on a surface of said electromagnetmeans and projecting towards said anchor means.
 6. A brake as claimed inclaim 1, wherein said stopping means comprises at least one springloaded pin operatively disposed in said electromagnet means andprotruding a predetermined distance towards said anchor means, afriction force between said pin and said anchor means being sufficientto prevent further rotation and advance of said electromagnet means insaid thread means.
 7. A brake as claimed in claim 1, wherein saidstopping means comprises at least one spring loaded pin operativelyextending through said anchor means and protruding a predetermineddistance towards said electromagnet means, a friction force between saidpin and said electromagnet means being sufficient to prevent furtherrotation and advance of said electromagnet means in said thread means.